Gap frame press



Oct. 20, 1953 E. K. JoHANsEN 2,656,028

GAP FRAME PRESS Filed June 3. 1949 9 Sheets-Sheet l Hf lave/27%? //FQP M550/25612 O ct. 20, 1953 E. K. JoHANsEN 2,656,028 GAP FRAME PRESS I Filed June 5. 1949 9 Sheets-Sheet 2 Oct. 20, 1953 E. K. JoHANsEN 2,656,028

GAP FRAME PRESS Filed June 5. 1949 9 Sheets-Sheet 5 =fund Oct. 20, 1953 v1-:. K. JoHANsn-:N 2,656,028

GAP FRAME PRESS Filed June s, 1949 9 sheets-sheet 4 Oct. 20, 1953 E.l K. JoHANsrv-:N 2,656,028

GAP FRAME PRESS Filed June 3.- 1949 9 Sheets-Shed'I 5 f E. K. .loHANsEN GAP FRAME PRESS 9 sheets-sheet e Oct. 20, 1953 Filed June 3. 1949 Oct. 20, 1953 Filed June 3, 1949 E. K. JoHANsEN 2,656,028

GAP FRAME PRESS 9 Sheets-Sheet. 7

Oct. 20, 1953 E. K. JoHANsEN 2,656,028

GAP FRAME PRESS Filed June 3, 1949 9 Sheets-Sheet 8 V/,\\l||nf////////////l 123 fig/4 lIIII\lI7///7///////A ID i @WWW/QM 9 Sheets-Sheet 9 E. K. JoHANsEN GAP` FRAME PRESS Oct. 20, 1953 Filed June 3. 1949 Patented Oct. 20, 1953 UITED STATES PATENT OFFICE 2,656,028 GAP FRAME PRESS Application June 3, 1949, Serial No. 97,057

1 Claim.

This invention relates in general to a new and novel form of operating mechanism for metal working presses, and is illustrated herein particularly adapted for use in connection -with the operation of a gap frame press.

The principal object of the present invention is to provide a novel form of actuating mechanim for the reciprocating slide of a metal working press which can be adjusted for either repeat operation or for single cycle operation.

Another object of the invention is to provide an actuating mechanism for a metal working press which is pneumatically controlled and wherein air is caused to cycle the machine either once or repeatedly as desired in accordance with an adjustment which may be made on a part of the mechanism.

A further object of the invention is to provide a pneumatically operated actuating mechanism for reciprocatingr the slide of a metal working press wherein air is caused to simultaneously engage a clutch mechanism and release a brake mechanism for cycling the press.

Still another object of the invention is to provide a novel form of mechanism for automatically stopping the reciprocation of the slide in the press at the end of a single cycle.

A still further object of the invention is to provide operating mechanism for a metal working press wherein a pneumatic system is `caused to actuate the siide of the press, and wherein an adjusting device may be set to permit either a repeated cycling of the machine or to prevent the cycling of the machine more than once.

Other objects and advantages of the invention will become apparent from reading the following description taken in conjunction with the accompanying drawings in which:

Fig. 1 is a side elevational view of a gap frame press showing the present invention applied thereto;

Fig. 2 is a front elevational View of the press shown in Fig. l with ycertain parts broken away and shown in section for the sake of clarity;

Fig. 3 is a fragmentary rear elevational view of the press shown in Fig. 1 and showing only the upper part thereof;

Fig. 4 is an enlarged fragmentary elevational View of the brake mechanism with portions thereof shown in section for the sake of clarity;

Fig. 5 is a fragmentary top plan view of the machine shown in Fig. 1;

Fig. 6 is a fragmentary side elevational view of 'the upper part of the machine shown in Fig. 1 with a part of the frame broken away to show the air valve operating mechanism more clearly;

Fig. 7 is a side elevational View of the clutch mechanism with parts broken away substantially along line 'l-'i of Fig. 8;

Fig. 8 is a horizontal sectional view through the clutch mechanism and flywheel taken along line 8-8 of Fig. 2;

Fig. 9 is an enlarged side elevational View of the actuating mechanism for the pneumatic system shown in non-actuated position with the front plate removed therefrom and with certain parts shown in section for the sake of clarity;

Fig. 1() is a top plan view oi the mechanism shown in Fig. 9 with a portion thereof in section to show certain details;

Fig. 1l is a View of the actuating mechanism similar to Fig. 9 with the parts shown inY actuated position;

Fig. 12 is a view of the actuating mechanism similar to Fig. 11 but showing the parts adjusted for continuous and repeated cycling of the machine;

Fig. 13 is a front elevational view of the actuating mechanism shown in Figs. 9 to 12, inclusive;

Fig. 14 is a horizontal sectional View taken along the line lli--I 4 oi Fig. 13;

Fig. 15 is a horizontal sectional view taken along line l5-I5 of Fig. 9;

Fig. 16 is a side elevational view of the air valve and actuating mechanism therefor;

Fig. 17 is a top plan view of the mechanism shown in Fig. 16 with a portion thereof in horizontal section taken along line IT-I'l of Fig. 16; and

Fig. 18 is a rear elevational view looking toward the left in Fig. 16 but lwith the supporting bracket removed therefrom to more clearly show certain details.

The operating mechanism for actuating the reciprocating slide of a metal working press may be adapted for use in any type of press where a reciprocating slide is caused to perform work upon a workpiece positioned on a die block. The illustration in the drawings of this mechanism as applied `to a gap frame inclinable press is primarily for the purpose of showing the application of the invention and is not intended to be limiting.

The reciprocating slide of the press is adapted to be driven by a rotating shaft having a crank portion thereon. Continuously operating drive means is adapted to be connected to the rotatable shaft by means of a clutch mechanism when it is desired to have the machine cycle.

A brake device is also associated with the rotatable shaft and is normally applied to the shaft to prevent rotation thereof except when the clutch is engaged. A novel form of. pneumatic system is embodied in the invention for simultaneously applying air to the clutch and the brake. When the air is thus applied, the brake releases the rotatable shaft and the clutch engages the drive means with the shaft to cause the shaft to rotate and cycle the machine by reciprocating the slide member.

The invention also embodies a novel form f actuating mechanism for the pneumatic system. This actuating mechanism is operable upon movement of a treadle. 'An adjustment is also provided on the operating mechanism for either continuous operation or non-repeat operation of the machine. When the adjusting mechanism is in the non-repeat position, the machine operator may press the threadle and immediately release the treadle, whereupon the; machine will cycle once and then automatically stop. When the adjustment is in the position for ,continuous operation, the operator presses the treadle' once and then releases the treadle, whereupon the machine will cycle continuously through the repeated reciprocation of the slide member.

Referring now more particularly to the drawings, and especially to Figs. l, 2 and 3, there is illustrated a conventional gap frame inclinable press comprising a base member I having spaced sides 2 between which sides a main frame 3 is mounted for pivotal movement about a pivot rod 4. The sides 2' of the base are provided with a plurality of openings spaced apart on a radius from the pivot point 4 and are adapted to receive a retaining bolt or rod 5. This rod 6 also is secured to the frame 3 and by inserting the retaining rod 6. in the different openings 5, the frame 3' may be tilted or inclined about the pivot point 4 for different operations.

A supporting rod 1 is secured at the rear of the frame by means of the. pin t3` at one end thereof' and the pin 9 at the bottom end to aid'` in supporting the frame when it is being inclined and for holding it in an inclined position.

The front of the frame 3' may be provided with a lower die block Il! and an upper die block Il. The upper die block is a part of a reciprocating slide member Ha adapted to reciprocate in the guideways I2 at each side. of the. frame. The upper end of the slide I' la; is provided with a shaft or pin I3 which is received by the. lower end of a crank arm i4. The. upper end of the crank arm I4 receives a crank portion I5. intermediate the ends of a rotatable. drive shaft i6. The drive shaft I6 is journaled in. bearings i1 and I8 at opposite sides. of' the frame A brake mechanism generally indicated at` 19t is operably associated with the drive shaft IB adjacent. one end thereof and is normallyy applied to the shaft to prevent rotation thereof'. A flywheel 20 is mounted at the opposite end' of drive shaft I and has associated therewith a clutch mechanism 2|'.

One or more drivel belts. 2-2 passv around the flywheel 23; and a pulley 23, which pulley 2.3 is mounted on a shaft 24 connected to the motor 25 at the rear of the press. The motor 25 is suitably secured to a mounting' bracket 26 mounted on the frame 3.. Operation ofthe motor 25 will therefore result in continuous. rotation; of the flywheel 2G. and its. connected parts;

A main airA conduit -21 (Figs. 5 and 6') supplies airV to the pneumatic system forv operating; the

clutch and brake devices. An air conduit 28 is connected to the main line 21 and has a valve associated therewith in the form of a slidable sleeve 29 surrounding the conduit 28. The details of this air valve will be described more fully hereinafter and is illustrated in Fig. 16. The branch conduits 38 and 3| are connected on the opposite side of the valve 29, the air conduit 3! being adapted to supply air to the clutch mechanism 2|, and the air conduit branch 3l being adapted to supply air for operating the brake mechanism I9.

The clutch mechanism The details of the clutch mechanism are more clearly shown in Figs. '7 and 3, to which refer- .ence Will now be made. A bushing 32 surrounds the driving hub 33 keyed to the shaft I5 by means of the key 34. A ring member 35 is fastened to the outer side of the flywheel 25 by means of a plurality of axially extending pins 36 thereby keying the ring 35 to the flywheel 2li. An outer plate 31 is secured to the flywheel 2t by means ofV a plurality of bolts 38 which also pass through the ring 35 and thereby secure the ring 35 in place as well as the operating mechanism for the clutch positioned between the plate 31 and the ywheel 2li.

The outer plate 31 has an inwardly extending annular rib 39 within which a ring 4i) is received. This ring 40 is utilized to clamp the peripheral edge of a diaphragm 4|, the ring and diaphragm being held in place by bolts 42 passing through the ring and diaphragm and extending into the inner face of the plate 31.

A clutch piston 43 isV mounted for axial movement within the housing formed by the ring 35 and isv located immediately adjacent the diaphragm 4l. The clutch piston 43 is provided with teeth 44 around the periphery thereof adapted to engage similar teeth on the inner surface of ring 35, whereby the clutch piston is splined to the ring 35 and may be moved in an axial direction...

A plurality of coiled compression springs 45 are located around the clutch piston 43 and extend in an axial direction. One end of each spring 45 bears against the inner face of the clutch piston 43 and the other end bears against the outer face of the ywheel 23, thereby normally urging the clutch piston out of engagement with the driving plate and driven plates as'V will. be presently seen` A driving plate: 4B surrounds the outer end of the driving hub 33 and is also provided with teeth 41 around the peripheral edge thereof whereby it' maybe also splined to the ring 35. Driven plates 48 and 49 arey splined to the outer end of the driving hub` 33V by means of the interlocking teeth 50 and thereby form a driving connection between the driven plates and the driving hub.

In the operation of thei clutch mechanism, the flywheel is beingY continuously rotated by the motor 25. The housing ring 35 and outer plate 31:' beingY connected to the' flywheel 20 will also be caused to rotate continuously. The clutch piston 43 and' driving plate` 46 are splined to the ring 35 and` alsov continuously rotate with the flywheel 20. None ofi these elements, however, have any connection withv the shaft IS so that the shaft will not be caused to rotate until the clutch is engaged. When. it is desired to cycle the; machine, air is caused to enter through the conduit 3.0. and. against. the outer face of. the diaphragm 4I. It will be noted that a small space is provided between the inner side of the plate 31 and the outer face of the diaphragm 4I so that when air enters this space, the pressure against the diaphragm will be equalized and will cause the diaphragm to move inwardly or toward the right as viewed in Fig. 8. This movement of the diaphragm will cause a similar axial sliding movement of the clutch piston 43. This axial movement of the clutch piston 43 will cause the driven plate 43 to be clamped between the clutch piston and the driving plate 46. The driven plate 49 will also be clamped between the driving plate 46 and the outer faceof the fly-l wheel 2l), thereby causing rotation of the driven plates 48 and 49. These driven plates have a driving connection with the driving hub 33 which is keyed to drive shaft I6 and will thereby cause rotation of the drive shaft and a reciprocation of the slide I I a through the medium of the crank mechanism I3, I4 and I5.

The brake mechanism The brake mechanism is illustrated generally by the numeral I9 in Figs. 1 to 6, inclusive, but the details thereof are more clearly shown particularly in Figs. 4 to 6, to which reference will now be made.

The brake mechanism includes a brake drum 5I mounted adjacent one end of the drive shaft I6 and a pair of arms 52 and 53 secured to each other at one end by means of a pivot pin 54. Each arm 52 and 53 has a circular portion to which the brake lining may be applied so that when the two arms are urged toward each other, the brake lining on each arm will be forced against the brake drum 5I to prevent rotation of the drive shaft I6.

One arm 52 of the brake mechanism is provided at its outer end with a recess 55 in which a plunger member 56 is adapted to slide. A cupshaped member 51 is caused to bear against the inner end of plunger 55 by means of a disc 58 mounted on a bolt 59. The end of bolt 59 is secured to the plunger 56 by threadedly engaging an opening in said plunger. A coiled compression spring 60 bears at one end against the disc 58 and at its other end against the bottom of the recess 55, so that the plunger 56 will be normally urged outwardly to bear against the end 6I of the other arm 53 of the brake mechanism.

An elongated rod 62 extends through both arms 52 and 53 and has a nut 63 threadedly engaging the outer end thereof. The closed end 64 of a tubular plunger 65 bears against the nut 63 and the plunger is mounted for bodily sliding movement axially thereof within a recess 66 in the arm 53. A coiled compression spring 61 surrounds the rod 62 and bears at one end against the bottom of recess 63 and at its other end against the bottom S4 of the tubular plunger 65. The action of spring 61, which is considerably heavier than spring 60, will urge the two arms 52 and 53 together so that the brakes will be normally applied to prevent rotation of the drive shaft I5.

When the air valve is open for operation of the machine, air will be caused to enter the recess 55 through the conduit 3| and apply pressure against the disc 58. When the pressure of the air within the recess 55 plus the pressure created by spring 69 is sufficiently great to overcome the resistance of spring 31, then the two brake arms 52 and 53 will be caused to sepa- 6 rate, thereby releasing the brake and permitting rotation of drive shaft I6.

As wil1 be seen later, the air in the pneumatic system is caused to flow simultaneously through conduit 3B to the clutch mechanism and through conduit 3| to the brake mechanism so that the clutch will be engaged to drive the shaft I6, as above explained, at the same time the brake is released to permit the shaft I6 to be driven.

Air valve actuating mechanism Reference will now be made particularly to Figs. 16, 17 and 18 disclosing the details of the air valve and the actuating mechanism therefor.

It was previously stated that the air valve constituted a slidable sleeve member 29 around the air conduit 28. This sleeve member has an annular recess or groove 58 around the outer surface thereof adapted to receive the inwardly extending lingers 69 secured to the ends 19 of a bifurcated member or yoke 1I. The opposite end of the yoke 1I is provided with spaced apart sides 12 extending on opposite sides of a bracket member 13 to which it is pivotally mounted by means of the pivot pin 14.

An actuating link 15 is pivotally secured as at 16 at its lower end between the sides of the yoke 1 I. The link 15 includes spaced apart side members between which a pivot pin 11 is adapted to be located and which passes through the end 18 of a rod 19. The opposite end of rod 19 terminates in a circular disc-like portion received within a recess 3I in the bracket 13. The circular disc-like portion 80 will permit an up and down movement of the horizontal rod 19 about one end thereof as a pivot, and will cause the link 15 to raise and lower.

A coiled compression spring 82 bears at one end against the end 19 on the rod 19 and at its other end against the disc 80, to thereby normally force the sides of link 15 in a counterclockwise direction about the pivot pin 16.

Another pin 33 connects the two sides of the link 15 at its upper end and is adapted to bear against the two sides 94 and 85 of a cam member 35. The cam member 86 is an integral part of a collar 81 mounted on a vertically extending longitudinally reciprocating rod 3S. rihe rod is mounted for vertical sliding movement within the bearing portions 89 and 99 of the supporting bracket 13. The spring 82 urges the link. l5 and the pin 33 toward the left as viewed in lo so that the pin 93 will bear against either the surface 34 or the surface 35 of the cam member 35. When the rod 33 is caused to move downwardly, the cam member 955 and its collar 31 will also move downwardly and will force the link 15 together with pin 83 toward the right in a clockwise direction about the pivot pin it. The rod $9 will move downwardly but a short distance so that after the Ipoint of the converging surfaces 84 and 85 of the cam member 83 has moved below the center of pin B3, the pin 83 will ride upwardly along surface 35 of the cam to elevate arm 19 about the disc 59 as a pivot point. This movement will elevate the yoke ll and will canse a clockwise movement of the yoke about its pivot pin 13 to elevate the sleeve 29 of the air valve.

A coiled compression spring 9i surrounds the rod S3 and bears at one end against the bearing member 99 and at its other end upwardly against the collar 81. The spring @I thus normally urges the rod 8B in an upward direction.

rllhe lower end of rod 38 below the bearing 93 threadedly engages a link member 92 having spaced; 'apart S3. linie '5a is; connected between the sides ofi link s3;- by means.. ofA the-.pivotpin55.; linkagemechanism is conminted to'I an operating device presently to be described which adaptedz to raise and lower the rod 38 andf yoke 'I:I` together with theY sleeve 28 for the purpose ofl actua-ting the air valve and causing air u-nderpressure: to flow to the clutch andY brake mechanisms..

IThe air conduit 28 (Fig. 16) has a partition 9B therein at a suitable location and the wall thereof is provided with a port 97 above the partition 535'-, `and with another port 98 below the partition 96. The sleeve 2Q has. an interior diameter larger thanthe conduit 28`so as to provide an annular air passage 9s between the sliding sleeve 29' of the valve andthe conduit 28.

Air from the main line 2T is directed upwardly through the conduit 28' and' outwardly through the port 9i? into the annular passage 53. When the sleeve 29T of the air valve is in normal position, however, air will be conne'd within the valve until the sleeve 2Q is moved upwardly to actuate the air valve. When the sleeve 29 is moved upwardly by a clockwise rotation of the' yoke 'II due to downward. movement of the rod 88., whereby the pin 83 will be caused to climb upwardly on the inclined surface S5 of the cam member 85, the sleeve 2.9' will assume the dotted line position shown in Fig. 16 where the upper port all' will be in communication with the annular passage 9S within the sleeve. rihe air under pressure will then beY free to pass outwardly through. port 98 into th'e annular passage Sti and inwardly throughv the port 9i through the conduits Se and 3i' to the clutch mechanism 2| and the brake mechanism respectively. As long as the valve is in this actuated' position, air will be forced into the conduits 30 and 3l to engage the clutch and release the brake, thereby causing rotation ofthe drive shaft" I6 and a cycling of the machine.

At the end of any given cycle when rod 318 is caused to move upwardly, pin S3 will ride downwardly over the inclined surface 85 of cam 86 and will continue to ride downwardly along the lower inclined surface 8 of the cam member, thereby moving the yoke il downwardly together with the sleeve 29 of the air valve cutting off communication between the two ports 9S and 97. This will result in a disengagement of the clutch mechanism and an application of the brake mechanism to immediately stop any further rotation of the drive shaft i6 and will prevent any further operation or cycling of the machine.

The operating device for the ai?" valve actuating mechanism rEhe operating device for the air valve actuating mechanism is connected directly with the treadle which the machine operator presses for cycling the machine. An understanding of the connection between the actuating mechanism for the valve and the present operating device may be had by reference to Fig. 6 wherein it will be seen that an arm Ill is pivotally secured at one end thereof by means of the pivot pin Il to the lower end of link 54. The other end of arm I is secured to a shaft |2 which is mounted for a rotary movement in a bearing or hub portion |63 extending outwardly from one side of a plate |013 (Fig.

This operating device is shown. in more detail in Figs. 9- to 15, inclusive.v The plate loll from which the bearing IBS extends is separated from the-main frame; s bymeans of-V spacer Amembers |85, VIlli and Il!!! (Fig: :13). Suitable securing screws arey applied tofasten-the plate Iflltothesespacer members .on the. .main frame. The plate Ill is provided with la plurality of bosses such.. as. |98 and. I'll9so that an outer cover plate Iii may be secured thereonand in. spaced relation thereto.

The rockableshaft |02 has secured thereto an actuating member ||f| with an arm I I2 extending. tangentiall-y therefrom, (Figs. 9, 10 ll and 125;.. As viewed in Figs. v9, L1 and 12. the arm H2 is normally urged.v `and `maintained upwardly by. means of a spring pressed; plunger I I3 adapted tov move axially in the recess of a. cylindrical boss.

lili on the plate |54, at. thefbottom thereof. The. bottom of. the opening. in boss Ht is. closed by a plug. H5.. The plunger H3. is normally urged upwardly against the.- arm 'H2 of the actuating. member Ill by means of a. coiled compression spring IIS which bears at its. bottom end against the plug H5 and upwardly at its upper end against a part ofv the plunger Hf. This arrangement gives the. actuating member Iii a normal position as shown in- Fig. 9,. but. permits a clock.- wise` rotation. of themember il! together with the shaft |532- on` which it is mounted for a limited distance.

Immediately adjacent the outer end of arm ||2 on` the actuating member there is a vertically extending thrust member or link` |.|.`I mounted by means of the pivot pin I I8 to an arm H. The arm YI IS is mounted at one endthereof to4 astub shaft |28.. A plate or lever |21 having a substantially triangular configuration is also mounted at one corner thereof on the. shaft |20 and is .mounted for an oscillating movement throughout a limited distance about said shaft.

The armlI'S constitutes the settable mechanism for determining whether the machine is to be set vfor continuous operation or for non-repeat operation. Fig. 9- illustrates the various parts inthe non-repeat position. The arm I9 is mounted for movement with the lever |2|V through the medium of a connecting pin or plunger member |22 (Fig. 1.0). This plunger |22 is counted forl limited. axial movement within a bearing member |23 threadedl-y engaging an opening in the arm I Ill and. extending outwardly into the outer face plate IIQ. The plunger |22 has a stem |24 extending outwardly therefrom and is provided with asmall circular handle portion lf2-5 at its. outer end. A coiled compression spring, |126 is located around the stem |24 and within the bearing |23. 'One end of spring |2S- bearsV inwardly against the plunger portion |22 and outwardly against a shoulder on the inner surface of bearing #23 so that the plunger |22 will be normally urged inwardly. There are two holes |21 and |28/ in the lever I2I. The upper hol-e I2." is adapted to receive the plunger I22 and connect arm H9 with the lever I2| so that when lever* I2.| is caused. to oscillate about shaft |20, the: arm IIS will' be moved therewith. Movement ofvr lever |12Iv and arm t9 will carry with it the link II'I. When it is desired to have continuous uninterruptedoperation of the machine, the handle portion |25 will be grasped by the operator and pulled outwardly to remove the plunger |22 from hole |27. Movement of the arm I I 9 may then be had to move the arm downwardly and` connect arm` H9 with lever |2I by movement of the plunger |22' into the hole 28.

As will be presently seen, this sets the machine for continuous operation.

The outer end of lever I2| is provided with a pin |29 to which is secured a link I 3|) and an operating rod I3I. This operating rod |3| extends downwardly and is connected to a treadle |32 (Figs. 1 and 2) so that when the treadle is depressed there will be a movement downwardly of rod ISI and a similar movement of the lever |2| in a clockwise direction about the shaft |25 as an axis. This movement will force the thrust member II1 downwardly so that in the position 'shown in Fig. 9, the shoulder |33 on the link will come against the arm ||2 on the actuating member I II to rotate this member in a clockwise direction.

The thrust lever ||1 is also provided with a similar shoulder |34 for use in actuating the air valve for continuous operation. There is also a recess |35 in the same side of link II1 for a purpose which will be presently described.

The thrust lever II1 is urged against the arm ||2 of the actuating member by means of a spring pressed plunger |345. This plunger |35 is mounted. in a tubular bearing member or boss |31 formed in the bracket and is closed at one end by a plug |38 threadedly engaging the internal threads thereof. The plunger |36 has a stem |39 supported by an opening |40 in the plug |38. A coiled compression spring |4| bears at one end against the inner end of plug |38 and at its other end against the shoulder formed between the plunger |35 and the stem part |39 thereof. The plunger |35 is in alignment with the rear edge oi the thrust lever |I1 and bears thereagainst to normally urge the thrust lever ||1 in a clockwise direction about its pivotal mounting IIS to force the forward edge thereof against the arm I2.

When the treadle |32 is depressed, a suitable linkageA mechanism exerts a downward pull on rod I3! to urge the lever I2| downwardly about its pivotal mounting at |25. Arm IIS being connected to lever |2| will move downwardly therewith, thereby also moving the thrust member I I1 downwardly. When the arm IIS is in the nonrepeat position as shown in Figs. 9 and 11, downward movement of the thrust lever I I'I will cause shoulder |33 to come against arm |I2 and rotate the actuating member III in a clockwise direction to the position shown in Fig. 11. This will cause a clockwise rotation of shaft |02 as viewed in Fig. 6 and a downward movement of link 54 and rod 38. Referring to Fig. 16, it will be seen that downward movement of rod 38 will cause a like movement of the collar 81 and cam 85 connected thereto to thereby cause the pin 83 to ride upwardly along the inclined cam surface 85 to raise the yoke 1| about its pivot point i4 and a similar upward movement of the valve sleeve 29. The port 91 will thereupon be in communication with the annular passage 99 in the valve, whereupon air under pressure will be directed to the clutch and brake mechanisms heretofore described.

Immediately adjacent link II1 Figs. 9, 11 and 12 is a holding latch member |42 pivotally mounted to the bracket at |43. This latch member |42 is provided on its forward edge with a shoulder |45. The member also has a pin |46 on one side thereof in the path of movement of the thrust member I I1.

A spring pressed plunger |41 is adapted to bear against the rear edge of the holding latch |42 to normally urge the holding latch toward the left and against the arm ||2 of the actuating member III. This plunger construction is simi'- lar to the one just described which holds the thrust member I|1 against the actuating arm, and includes a tubular boss |48 on the bracket closed at one end by a plunger |45. The plunger |41 has a stem portion |55 adapted to ride in a suitable opening in the plunger |49. The coiled compression spring I5I which surrounds the stem portion |58 bears at one end against the inner end of plug |49 and at its other end against the shoulder formed between the plunger |41 and the stem |50. The spring |5| thereby normally urges the plunger |41 outwardly and holds the holding member |42 in contact with the actuating arm I I2.

When the thrust member ||1 is moved downwardly to rotate the actuating member III and to position the arm ||2 in a substantially horizontal position as shown in Fig. 11, the holding latch |42 will move about its pivot point |43 in a clockwise direction under the influence of the plunger |41 so that one of the shoulders |44 or |45 will come against the upper edge of arm ||2 and hold the actuating member III in the operating position. This will hold the rod 88 in a down position to maintain the air valve open for passage of air to the clutch and brake mechanisms. The operator of the machine may depress the treadle and immediately allow it to raise again, thereupon raising the thrust member II1. The actuating member |I| will, however, be held in its actuated position by means of the holding member |42 in the manner just described.

A trip member in substantially the form of a bell crank is generally indicated at |52 and is also mounted on the shaft |25 ior slight rotation thereon. The trip member |52 has three arms thereon indicated at |53, |54 and |55. The entire member |52 is normally urged in a clockwise direction around shaft |25 by means of the spring pressed plunger |55 which bears against the forward edge of arm |55. This plunger arrangement is similar to those previously described and includes a tubular member |51 within which the forward end of the plunger is adapted to ride. The outer end of the tubular member |51 is closed by a plug |55 and has a passage therein to permit a sliding movement of the stem |53 on the plunger |55. A coiled'compression spring 55 surrounds the stem |55 and bears at one end against the inner end of plug |58 and at its other end against the shoulder iormed between the end of the plunger |56 and stem |59. Thus the plunger is normally urged outwardly against arm I55 to rotate the member |52 in a clockwise direction.

Arm |54 has a pin IGI protruding from the rear edge thereof and is adapted to come against the forward edge of thrust member II'I for the purpose of stopping operation of the machine. Arm |53 is provided with a cam roller IGZ in the path of a cam member |63. This cam member |63 is mounted for rotation with the drive shaft IE as may be seen in Fig. 2. The cam |63 has an enlarged portion |64 thereon and rotates in a counter-clockwise direction as viewed in Figs. 9, 1l and 12. The position of this enlargement |64 in these iigures is the position thereof before the machine begins to cycle. When air is applied to engage the clutch and release the brake, the drive shaft I6 will rotate carrying with it the cam |53. One revolution of the cam will be substantially completed when the enlargement |64 comes lll against the cam .roller |62. Continued rotation oi the cam will rotate the "member |52 in a counterclockwise direction l,against the pressure of plunger' Hit` and will move arm '|54 'toward the right -t'o the dot-dash line ,position shown in Fig. 1l.. 'Ifhis movement toward the right of the arm |54 will cause the pin Ill'to come against the .torward edge of the thrust member I7 and move this thrust member toward 'the right until it comesagainst the pin |66 vin the 'holding latch |52.' Continued 'movement of arm |54 toward 4theriglit Vwill thereafter rotate the holding mem- 'l2abou't its supporting pin H53 in a counterclockwise direction, thereby moving 'the shoulder [Riou/tof engagement with the upper edge of theA actuating arm ||.2. The plunger H3 will thereuponA voperate to` move' the actuating member back'to 'its original positionand will rotate 4t he'shaft |02 ina counter-clockwise directo .elevate r`od`88 and Ycam member '86 'therewith, v'These ,parts will 'then 'be 'in the ,position ,shown in'Fig. 16A Where the pin 83 Ihas 'been caused to ride downwardly on the'lower inclined 'st'u'rffakie '8d of the cam member "S6 'to lower 'the .yoke'rl and move the valve sleeve 2li downwardly tdeut off Vcommunication "between the annular passage@ and port 97'. The clutch mechanism will thereupon'become 'disengaged andthe brake `be`applied Ato immediately stop rotation of 4thel'drive shait 'IB and will cause the cam |63 to again stop Vsubstantiallyin the position shown'in Figs'l 91151 .and `1`2.'

rIt will .thus be 'evident that .with the arm H5 in `theelevatedv position shwn'in'Fig. r9 with respect .to lever |-2 .the machine will beset 'to A`operatethrough' a single cycle'lon'ly, and 'hence may'oe termed the nen-'repeat position of the lshettalle device. "When lthe o'p'erator presses the tfeadl'e, the -holding latch 'I l2 will "hold the air .va eopen'to operate the drive sha'ft through one revolution therebyfcausingthe reciprocating slide memberltoniove downwardly and then upwardly. tthe' end of .one revolution of Ythe drive shaft, :the enlargement .[611 on thecam |63 will disen- Ygag' e thehldinglatch `|2 from the actuating vxierber l| toautomatically vclose the air valve landcause disengagement of the clutch and. ap- .'plication'dithe brake. "WWh'enitis,desiredtolhavethe machine operate eontinuc'uisly,r` the pin I |22 which forms a connec- .t'iohfbetweenarm i,9,-an`dplate- '2 may'be'with- .llrawnffrom'opening 4| 2'| and moved downwardly 'engage' opening 1.28. This position of these F1i'arts'fisshownin Fig12. When. this occurs, the '.thrust'member II will also be lowered so that theshoulder'l''ll ontheforward edge thereof will c'me'a'g'ainst the actuating arm 'I |2 to rotate the -member and Yshaft |02-in a clockwise 'direc- Ltinffto'lower the'ro'd '38 and open the valve. yAfgainf plunger ll'l 'will urge the holding latch |l2i`n` a clockwise 'direction'sothat the shoulder .'l4'5`-w'ill engage the' arm'l42 to "hold the valve lopen. At this point the recess |35 in the edge o'f thelthrust member |'l willbe opposite the pin lll. -`Thus, when the enlargement |64 on the .cam |63` engages the cam roller |62 and moves the trip'member |52 'in a counter-.clockwise dirre'ctio'n'the 1pin`|6| will assume the dotted line 'position of Fig. 12 and will move into the recess '|'35 without engagin'g'the thrust member ||1.

'The valve will thus remain open andthe machine willcontinue to operate aslong as the operator maintains l'thetreadle depressed. Upon release -treadlelA however, the thrustvmember Il will be elevated and the recess |35 moved out of Y 12 register with the pin |6j| s o that when the trip member |52 is next engaged bythe cam -rnember |63 the pin |161 will engage the side of fthethrust member 1 to trip the holding latch |42 in the .manner previously described.

From 'the fOregoing description it will be clear that therpiresrs may be set for either a single cycle operation or continuous operation. When v:the arm l.llil, is elevated so that `the pin |22 thereon is 'in engagement with opening i2? on the lever '|.2"| 'the machineis set for non-repeat operation. 'When the settable arm |9 is'lowered'so thatthe f2.2 is Yin engagement with opening L|28 'in lever 112|, the machine is then set for continuous operation, all in 'the manner above described. It will also be evident that the invention embodies ,novel mechanism 'for presetting the lmachine -for either non-repeat o-r continuous operation vby Aa pneumatic .system which causes vsimu'ltaneous engagement ci a'clutch and release of a brake for cycling `the machine. Automatic 4operation of .an .air valve at the completion of -one -cycle will apply the brake Yand disengage the lclutclfi simultaneously 'to stop further rotation of the .drive shalt.

Changes may be made inthe forni, construction yand arrangement of parts from that dis',- closed 4herein without departing from the spirit of the invetnion yor sacrificing `any of 'the attendant advantages 'thereonprovidedy however, that such changes 'fall -within the scope -of the lclaimappended hereto.

vThe,invention 'is hereby claimed asY follows ln a cyclically operable "machine 'of theI char- .acter described, a driving shaft, 'a drlven'fshait,

means operatively jconnect-ing said driven shaft vand.fn'iachine in -'driving relationship, a normally disengaged iluid pressure operated clutcliv'op- ,erativelylconnecting saiddriving shaiftianddriven shaftin driving relationship, ajnormallyengaged .fluid pressurev operated brake on said driving shaft, ,afsource o'f Iiluid under pressure, la normal;- ly.c'1osed valve connected -to--sai'd source 'andj oprable when open .to supply lluidirom saids'ourele to saidclutch and .brake to cause engagement .ofv the former and disengagement ci the latter, a, yvalve operating :member .operatively connected yto said' valve zand :movable from va retractedpo.- Asition. wherein thevalveisfclosed tc .an advanced position* wherein :thevalve is Open, means nor- -mally maintaining :said .member ,in .its :retracted posit-loma "depressible lever, a thrust :mei/uber, means selectively pivoting said 'thrust member tojsai'd 'lever at 'spaced points thereon whereby upondepressionofthe leverthefpositional movements of the thrustmember Ywill be -variedya `)pairro'i .shoulders en saidv thrust member selec- .tively'engageablewithsaid valve operating mem,- ber to ymovie .the .latter .to its.advancedl position upon f depression Y of saidlm ever,V s uciiY selectiviefengagementf depending yupon the selective i pivoting of said-,thrustl member, a holding -lratch engageable with said Valve operating member tofhold the` same inY its advanced 'rpo'sition, 1a trip :mem-

"ber -engageable with saidzlthrust :memberwvhen the-latter isin one of itsv selected pivotedfposi.- tionsj'forfmovingthe latter into engagement with s aidfholding latch to trip-fthe latter and release 'said 'valve `operating member, means on .fsaid thrust member for preventing enga-gement thereoff by said trpmember when the thrust'meniber isfin'its other selectedpivoted position, andcam means operable upon 'rotation of "said vvdriven EINAR K. JOHANSEN.

References Cited in the le of this patent Number UNITED STATES PATENTS Name Date Howland-Shearman May 5, 1936 Crley Sept. 1, 1936 10 Number 14 Name Date Mellon Dec. 29, 1936 Littell et a1 Aug. 31, 1937 Stout June 18, 1940 Crley Oct. 8, 1940 Friedman July 29, 1941 Crley Feb. 29, 1944 Eason May 16, 1944 Jonhe Sept. 27, 1949 Georgel Apr. 29, 1952 

